Turbine-Driven Fracturing System on Semi-Trailer

ABSTRACT

The present disclosure is directed to a system for fracturing operation in oil/gas fields. The disclosed fracturing system is integrated onto a semitrailer that can be conveniently transported to any oil field. The disclosed fracturing system further includes major components needed for delivering high-pressure fracturing fluid into a wellhead, including but not limited to at least one power generation source and at least one plunger pump driven by the at least one power generation source via simple transmission mechanisms utilizing reduction gearbox and/or transmission shafts. The power generation source, in particular, includes a turbine engine capable of being powered by 100% natural gasified liquid fuel. The fracturing system further includes hydraulic and cooling component for serving the various needs for the turbine engine, the reduction gearbox, and the plunger pump, such as lubrication of various moving parts

CROSS REFERENCE

This application is a continuation application of U.S. Pat. ApplicationNo. 17/829,881 filed on Jun. 1, 2022, which is a continuation orcontinuation-in-part of and claims priority to (1) U.S. Pat. ApplicationSerial No. 16/838,802, filed on Apr. 2, 2020, which is based on andclaims priority to Chinese Patent Application No. CN201910894306.9 filedon Sep. 20, 2019, (2) U.S. Pat. Application Serial No. 16/838,806, filedon Apr. 2, 2020, which is based on and claims priority to Chinese PatentApplication No. CN201910894342.5 filed on Sep. 20, 2019, (3) U.S. Pat.Application Serial No. 17/531,817, filed on Nov. 22, 2021, which is acontinuation of and claims priority to U.S. Pat. Application Serial No.16/832,191, filed on Mar. 27, 2020, which is based on and claimspriority to Chinese Patent Application No. CN201910894253.0, filed onSep. 20, 2019, and (4) U.S. Pat. Application Serial No. 16/832,205,filed on Mar. 27, 2020, which is based on and claims priority to ChinesePatent Application No. CN201910894228.2 filed on Sep. 20, 2019. TheseU.S. and Chinese Patent Application are herein incorporated by referencein their entireties.

TECHNICAL FIELD

The present invention relates generally to the technical field of oiland gas field operations, and specifically to a turbine-drivenfracturing system on a semi-trailer.

BACKGROUND

For extracting oil/gas by facture formation in oil/gas fields, a powersource may be configured to drive various fracturing equipment/systemsin various alternative manners.

The fracturing equipment may be driven by diesel engine(s). For example,a diesel engine may be connected/coupled to a transmission mechanismthrough a transmission shaft to drive a fracturing plunger pump togenerate and deliver high-pressure fluid into a wellhead for fractureformation. In other words, a diesel engine may be used as the powersource, whereas a transmission and a transmission shaft may be utilizedas the transmission devices, and a plunger pump may be used as thehydraulic pressure production element.

This example configuration may be associated with the followingdisadvantages:

-   (1) Large volume and excessive weight. When a diesel engine is    utilized to drive a fracturing plunger pump through a transmission a    transmission shaft, a relatively large equipment volume is needed.    The overall system is heavy, thereby redistricting transportation of    such systems and limiting the power density with respect to the    equipment weight;-   (2) Environmental impact. During operations at a well site, the    fracturing equipment driven by the diesel engine would generate    engine exhaust pollution and noise pollution. The noise may exceed,    e.g., 105 dBA and may severely affect the normal life of nearby    residents;-   (3) Cost inefficiency: The fracturing equipment driven by a diesel    engine requires relatively high initial purchase cost and incurs    high fuel consumption costs per unit power generation during    operation, and the engine and the transmission also require very    high routine maintenance costs.

Another driving mode may be based on electric-drive fracturing.Specifically, an electric motor may be connected to a transmission shaftor a coupling to drive the fracturing plunger pump. In other words, anelectric motor may be utilized as the mechanical power source. Atransmission shaft or a coupling may be utilized as the transmissiondevice, and a fracturing plunger pump may be used as the fracturingfluid displacement generation device.

Although the electric-drive fracturing mode may be associated with manyadvantages, it requires an electric power supply on fracturing wellsites. Generally, it is difficult to supply electric power to fracturingwell sites in that the typical electric power capacity at the well sitesmay be insufficient to drive the whole fracturing units, or there islack of power networks at well site. Therefore, for implementingelectric-drive fracturing, electric generators may be employed togenerate electricity. The most economical fuel for electricitygeneration may be natural gas. As such, natural gas electric generatorsmay be employed in order to control fuel cost. For a fracturing wellsitehaving no external power networks (e.g., electric grid), the powergeneration of a set of gas generators may need to be, for example, least30 MW. Gas electric generator with such capacity is usually exceedinglyexpensive. A single high-power electric generator also forms a singlefailure point.

SUMMARY

The present disclosure is directed to a system for fracturing operationin oil/gas fields. The disclosed fracturing system is integrated onto asemitrailer that can be conveniently transported to any oil field. Thedisclosed fracturing system further includes major components needed fordelivering high-pressure fracturing fluid into a wellhead, including butnot limited to at least one power generation source and at least oneplunger pump driven by the at least one power generation source viasimple transmission mechanisms utilizing reduction gearbox and/ortransmission shafts. The power generation source, in particular,includes a turbine engine capable of being powered by 100% naturalgasified liquid fuel. The fracturing system further includes hydraulicand cooling component for serving the various needs for the turbineengine, the reduction gearbox, and the plunger pump, such as lubricationof various moving parts.

In some example implementations, a turbine fracturing semi-trailersystem is disclosed. The turbine fracturing semi-trailer may include asemi-trailer body; a turbine engine comprising a rotational output endassociated with a first rotational axis; a first reduction gearboxassembly comprising a first planetary gearset engaging a parallelgearset engaging a second planetary gearset, the first planetary gearsetand the second planetary gearset being associated with a secondrotational axis and a third rotational axis, respectively; and a plungerpump comprising a crankcase associated a fourth rotational axis. Theturbine engine, the first reduction gearbox assembly and the plungerpump are sequentially disposed on the semi-trailer body. The firstrotational axis is colinearly aligned and coupled to the secondrotational axis; the third rotational axis is colinearly aligned andcoupled to the fourth rotational axis. The first rotational axis and thefourth rotational axis are offset from one another more horizontallythan vertically when the turbine fracturing semi-trailer system is in anoperational state.

In the implementations above, the turbine fracturing semi-trailer systemaccording to claim 1, wherein the first reduction gearbox assembly isintegrated with the plunger pump.

In any one of the implementations above, the turbine fracturingsemi-trailer system may further include a transmission device disposedbetween the turbine engine and the first reduction gearbox assembly.

In any one of the implementations above, the turbine fracturingsemi-trailer system may further include a second reduction gearboxassembly disposed between the turbine engine and the first reductiongearbox assembly.

In any one of the implementations above, the turbine fracturingsemi-trailer system may further include a transmission device disposedbetween the first reduction gearbox assembly and the second reductiongearbox assembly.

In any one of the implementations above, the transmission devicecomprises a single rotational shaft.

In any one of the implementations above, the turbine engine may furtherinclude an exhaust system disposed on an opposite side of the firstreduction gearbox assembly, and the exhaust system comprises an exhaustsilencer and an exhaust piping, the exhaust silencer is communicatedwith an exhaust port of the turbine engine through the exhaust piping.

In any one of the implementations above, the exhaust system, the turbineengine, the first reduction gearbox assembly, and the plunger pump aresequentially disposed in a straight line along a transmission directionof rotational power.

In any one of the implementations above, an air intake system may bedisposed on the semi-trailer body above the turbine engine. The airintake system comprises a plurality of air intake filters, an air intakesilencer, and an air intake duct. One end of the air intake silencer isconnected to the air intake filter. The other end of the air intakesilencer is connected to one end of the air intake duct. The other endof the air intake duct is connected to an air intake port of the turbineengine.

In any one of the implementations above, the plurality of air intakefilters may be disposed on two sides of the air intake system along adirection of power transmission of the turbine fracturing semi-trailersystem and extend at least an entire length of the turbine engine.

In any one of the implementations above, the turbine fracturingsemi-trailer system may further include a plurality of inertia separatorover the plurality of air intake filters for separating solid particlesand liquid droplets from air inflow into the air intake system.

In any one of the implementations above, the output power of the plungerpump may be 5000 hp or above.

In any one of the implementations above, the turbine fracturingsemi-trailer system may further include 3 or more axles installedbeneath the semi-trailer body, wherein each axel is installed with atleast a pair of wheels.

In any one of the implementations above, the turbine fracturingsemi-trailer system may further include a hydraulic power unit disposedon a gooseneck portion at one end of the semi-trailer body, thehydraulic power unit is configured to drive a hydraulic system in theturbine fracturing semi-trailer system.

In any one of the implementations above, the hydraulic power unit may bedriven by a diesel engine or driven by an electric motor.

In any one of the implementations above, a cooling system may becollocated with the hydraulic power unit on the gooseneck portion of thesemi-trailer body, the cooling system being configured to cool engineoil or lubrication oil displaced by the hydraulic power unit for anoperation of the turbine engine, the first reduction gearbox assembly,or the plunger pump.

In any one of the implementations above, the crankcase of the plungerpump may include at least 6 axle journals and at least 5 bellcranks.

In any one of the implementations above, a distance between a firstcenter of rotation of the at least 5 bellcranks and a second center ofrotation of a crankshaft of the crankcase may be between 120 and 160 mm.

In any one of the implementations above, a plunging stroke of theplunger pump may be between 10 and 12 inches when being in operation.

In any one of the implementations above, the plunger pump may bedisposed on a lapping section of the semi-trailer body and wherein thelapping section is configured with traction pin for attachment to atowing equipment for the turbine fracturing semi-trailer system.

Compared with the existing systems, the beneficial of theimplementations disclosed herein includes, among others, at least (1)the turbine engine, the reduction gearbox, the transmission mechanismand the plunger pump are connected in a straight line along thetransmission direction of power to avoid excessive transmission loss,thus ensuring efficient transmission performance; (2) the turbine engineis compact, light-weight, and of high-power density and thus for thesame outline dimensions and weights, the unit power of the turbinefracturing equipment can be more than twice that of conventional dieselengine fracturing equipment; (3) the turbine engine can use 100% naturalgas as the fuel directly, greatly reducing the fuel-cost compared to thediesel engines and no gas generator sets are needed; (4) the turbineengines drive the plunger pumps driven one-to-one with failure riskdistribution rather than having a single failure point; (5) thereduction gearbox design achieves high reduction ratio with a compactconstruction and integrable to the plunger box and with amulti-planetary gear design having a low center of mass.

The present invention will be described in detail below with referenceto the accompanying drawings and specific implementations.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 shows a schematic structural diagram of an example turbinefracturing semi-trailer system.

FIG. 2 illustrates a schematic structural diagram of an examplesemi-trailer-loaded turbine fracturing system.

FIG. 3 shows a schematic structural diagram of another example turbinefracturing semi-trailer system in an operation or storage configuration.

FIG. 4 shows a schematic structural diagram of the example turbinefracturing semi-trailer system of FIG. 3 in a transport configuration

FIG. 5 shows a schematic structural diagram of an example plunger pump.

FIG. 6 is a schematic structural diagram of an example reduction gearboxassembly.

FIG. 7 shows a cross-sectional view of an example planetary reductiongearset.

FIG. 8 shows a cross-sectional view of an example parallel reductiongearset.

FIG. 9 shows a schematic structural diagram of an example power endassembly of a plunger pump.

FIG. 10 shows a schematic structural diagram of an example crankshaft ina crankcase of a plunger pump.

FIG. 11 shows a schematic structural diagram of another turbinefracturing semi-trailer system in an operational or storage state.

FIG. 12 shows a schematic structural diagram of the example turbinefracturing semi-trailer system of FIG. 11 in a transport state.

DESCRIPTION OF THE EMBODIMENTS

The present disclosure is directed to a system for fracturing operationin oil/gas fields. The disclosed fracturing system is integrated onto asemitrailer that can be conveniently transported to any oil field. Thedisclosed fracturing system further includes major components needed fordelivering high-pressure fracturing fluid into a wellhead, including butnot limited to at least one power generation source and at least oneplunger pump driven by the at least one power generation source viasimple transmission mechanisms utilizing reduction gearbox and/ortransmission shafts. The power generation source, in particular,includes a turbine engine capable of being powered by 100% naturalgasified liquid fuel. The fracturing system further includes hydraulicand cooling component for serving the various needs for the turbineengine, the reduction gearbox, and the plunger pump, such as lubricationof various moving parts.

In comparison to traditional diesel engine-based or electric motor-basedfracturing systems, benefits of the system described in the presentdisclosure include at least: (1) lower power transmission loss (e.g.,because the turbine engine, the reduction gearbox, the transmissionmechanism and the plunger pump are connected in a straight line alongthe transmission direction of power, excessive transmission loss isavoided during operation, thereby providing efficient transmissionperformance); (2) smaller footprint, lower weight, higher operatingefficiency, and higher power density (e.g., the turbine engine issmaller and light-weight compared to traditional diesel engine, ordiesel engine-powered electric generator, and is thus characterized byhigher power density in that, for example, the unit power generated bythe turbine fracturing equipment disclosed herein can be more than twicethat of conventional diesel engine fracturing equipment with similardimensions, footprint, and weight); (3) lower operational cost (e.g.,because the turbine engine can directly use 100% natural gas, fuel costis greatly reduced in comparison to cost of diesel fuel in a dieselengine or equivalent cost of investment if a gas powered electricgenerator is used as the power source), (4) failure risk distributionand reduced downtime (e.g., because the turbine engine in the systemdescribed herein is usually operated with the plunger pump in aone-to-one correspondence with a simple transmission and couplingmechanism, power source failure risk at a well site utilizing multiplesets of such systems is thus lower due to risk distribution incomparison to a traditional system where a single high-power gaselectric generator set is used to drive multiple plunger pumps and wherethe system may suffer single-point failure).

An example turbine-based fracturing system disposed on a semi-trailerplatform is illustrated in FIG. 1 . As shown in FIG. 1 , the examplefracturing system may be implemented as a turbine fracturingsemi-trailer platform, including a semi-trailer body 1-3, a turbineengine 1-7, a reduction gearbox 1-8, and an integrated transmissionmechanism and a plunger pump 1-10, wherein the turbine engine 1-7functions as the power source of the power transmission system of theentire semi-trailer system. The turbine engine 1-7, the reductiongearbox 1-8, the transmission mechanism and the plunger pump 1-10 aredisposed on the semi-trailer body 1-3. The semi-trailer body 1-3 mayalso be provided with other components such as batteries,wiring/cabling, a fuel tank, a lubricating oil tank, a hydraulic oiltank and other components for providing service and support (e.g.,lubrication, cooling, and the like) for the other components such as theturbine engine 1-7, the reduction gearbox 1-8, and the plunger pump1-10. An output end of the turbine engine 1-7 may be connected to thereduction gearbox 1-8. The reduction gearbox 1-8 and the plunger pump1-10 may be connected through a transmission mechanism. The transmissionmechanism may be integrated with the reduction gearbox 1-8, as will bedescribed in more detail below (even though, in some other alternativeimplementations, the transmission mechanism may be separate from thereduction gearbox 1-8). In some other implementations as described belowthe reduction gearbox may be integrated with the plunger pump and insuch implementations, the output end of the turbine engine may beconnected to the reduction gearbox integrated with the plunger pump viaa transmission mechanism (a transmission shaft, or the like). Thereduction gearbox 1-8 is used to slow down the rotational speed andincrease the torque of the power output of the turbine engine 1-7 fordriving the plunger pump 10 via the transmission mechanism or directly.

The turbine engine 1-7 may be provided with an exhaust system disposedon an end of the turbine engine in an opposite side of the power outputend facing the reduction gearbox 1-8. The exhaust system may include anexhaust silencer 1-4 and exhaust piping/duct 1-5. The exhaust silencer1-4 may be coupled with a combustion exhaust port (or an exhaust port,for simplicity) of the turbine engine 1-7 through the exhaustpiping/duct 1-5. The exhaust piping/duct 1-5 may be used to directcombustion exhaust of the turbine engine 1-7 into the exhaust silencer1-4. The exhaust silencer 1-4 can be configured with flow dampingchambers and structures that help reduce noise generated by exitingcombustion exhaust during an operation of the turbine engine 1-7. Theexhaust silencer 1-4 may be alternatively referred to as an exhaustmuffler.

As shown in the example of FIG. 1 , the exhaust system, the turbineengine 1-7, the reduction gearbox 1-8, the transmission mechanism andthe plunger pump 1-10 may be disposed in a straight line along thetransmission direction of mechanical power. In particular, the turbineengine 1-7, the reduction gearbox 1-8, the transmission mechanism andthe plunger pump 1-10 are coupled in a straight line along thetransmission direction of power to avoid transmission complexity andexcessive transmission loss, thereby enabling efficient transmissionperformance. Moreover, such a configuration can lower the center ofgravity of the fracturing equipment on the semi-trailer body forachieving easier and more stable transportation of the semi-trailer. Theturbine engine 1-7 is by itself advantageous because of its smallersize, lighter weight and higher power density over direct-drive dieselengine or a combination of electric generator driven by a diesel engineor a turbine engine. For similar outer dimensions, footprint, andweight, the unit power generation of the turbine fracturing equipmentdisclosed herein can be more than twice of that of conventional dieselengine fracturing equipment. The turbine engine 1-7 can further directlyuse 100% natural gas as the fuel, which greatly reduces operating costof the system compared to the cost of diesel consumption associated withdiesel engine or the cost of gas generator sets when being used to drivethe plunger pump. The turbine engine 1-7 also can use 100% oil fuel orother types liquid fuels.

In addition, as shown in FIG. 1 , the turbine engine 1-7 may beconfigured to drive the plunger pumps 1-10 in a one-to-onecorrespondence. Unlike the implementations of electrically drivenfracturing equipment in which a single high-power gas generator set isused to drive multiple plunger pumps, multiple sets of the one-to-oneturbine plunger pump system described above in FIG. 1 can be used in anoil/gas field collaboratively and can effectively avoid single pointfailure. In other words, the failure risk is distributed such thatfailure of one turbine engine would not stop the entire fracturingsystem from continuing using other separate turbine engines whereasfailure of the single generator in the traditional system would shutshown the entire operation.

As shown in the example of FIG. 1 , an air intake system 1-6 is disposedon the semi-trailer body 3, the air intake system 1-6 includes an airintake filter, an air intake silencer and an air intake piping/duct. Oneend of the air intake silencer may be connected to the air intakefilter, whereas the other end of the air intake silencer may beconnected to one end of the air intake piping/duct. The other end of theair intake piping/duct may be coupled to and connected with an airintake port of the turbine engine 1-7.

In some implementations, the air intake system including the air filtersmay be disposed on top of the turbine engine and extended over theentire turbine engine 1-10 in a parallel plane of the semi-trailerplatform, as shown in FIG. 1 . In some implementations, the peripheralsof the air intake system along at least two sides indicated by theshaded area in FIG. 1 may be installed with continuous group of airfilters. In some implementations, additional inertia separatorstructures may be installed in front of the filters to remove solidparticles and liquid droplets from the intake air. External air flow mayflow through the inertia separator and the air filters into the airintake system and may be guided into the air intake port of the turbineengine 1-10.

The power of the plunger pump 1-10 may be designed and rated at 5000 hpor above. In general, the greater the power of the plunger pump 1-10 is,the more suitable it is to use the plunger pump for lone-time andhigh-load continuous operation conditions.

The transmission mechanism may be implemented as a transmission shaft1-9 or other types of coupling, as described in more detail below.

The number of axles of the semi-trailer body may be 3 or above, toensure an adequate bearing capacity. Each axle may be installed with twoor more wheels. As shown in the example implementation of FIG. 1 , atleast one of the axles may be disposed at the rear portion of thesemi-trailer underneath the plunger pump, as the plunger pump mayconstitute a relatively heavier component of the fracturing system.

As shown in the example of FIG. 1 , a hydraulic power unit 1-2 may bedisposed on a gooseneck of the semi-trailer body 1-3. The gooseneck ofthe semi-trailer in the particular example of FIG. 1 may be on theopposite end from the axels and wheels of the semi-trailer and may bewhere the semi-trailer can be attached to a tractor for transportation.The hydraulic power unit 1-2 may be used to drive the hydraulic systemon the turbine fracturing semi-trailer. The hydraulic system may includea hydraulic pump, a hydraulic motor, various valves, a hydraulic oiltank, a hydraulic oil radiator, etc. The main role of the hydraulicsystem is to drive the fuel pump of the turbine engine 1-7, the startingmotor of the turbine engine 1-7, the power end lubrication system of theplunger pump 1-10, the lubrication system of the reduction gearbox 1-8,various oil radiators and the like.

In some example implementations, the hydraulic power unit 1-2 may be adiesel engine, or another type of internal combustion engine, or anelectric motor. The diesel engine or other type of internal combustionengine may only be sufficiently configured to achieve the limitedfunction above. The electric motor, when being used, may draw power froma chargeable battery, or may be powered by electricity delivered to thewell site through, for example, an electric grid, or from a separateonside electrical generator system.

A cooling system 1-1 may be disposed on the gooseneck of thesemi-trailer body 1-3, the cooling system 1-1 may be configured to cooloils used on the turbine fracturing semi-trailer. The oils being cooledby the cooling system 1-1 include engine oil and the hydraulic oildescribed above for the turbine engine 1-7, lubricating oil for theplunger pump 1-10, lubricating oil for the reduction gearbox 1-8, andthe like. In some implementations, the engine oil or lubrication oil maybe circulated from the hydraulic system disposed on the goosenecksection of the semi-trailer body 1-3 to the cooling system and then tothe turbine engine 1-7 or the reduction gearbox 1-8, or the plunger pump1-10, and then back to the hydraulic unit. Alternatively, the engine oilor lubrication oil may be circulated from the hydraulic system disposedon the transport section/gooseneck section of the semi-trailer body 1-3to the turbine engine 1-7 or the reduction gearbox 1-8, or the plungerpump 1-10, and then to the cooling system, and back to the hydraulicunit.

FIG. 2 show an example for direct drive of the gearbox and plunger pumpby the turbine engine. As shown in FIG. 2 , the example power drivesystem may include a turbine engine 2-3, an exhaust system and afracturing pump 2-1, wherein one end of the turbine engine 2-3 isconnected to the exhaust system; and the other end of the turbine engine2-3 is connected to the fracturing pump 2-1. The fracturing pump 2-1 maybe integrated with a reduction gearbox 2-2. The turbine engine 2-3 maybe directly connected to an input end of the reduction gearbox 2-2 onthe fracturing pump 2-1. The power drive system for the fracturing pump2-1 is thus directly driven by a turbine engine 2-3, via the reductionbear box 2-2 without additional transmission mechanism. The turbineengine 2-3 can use 100% natural gas as the fuel rather than diesel fuel,thereby lowering fuel costs. In addition, the turbine engine 2-3 may beadvantageously associated with a small volume and light weight, whichgreatly decreases the overall volume, footprint, and weight of theentire power drive system for the fracturing pump 2-1.

As shown in FIG. 2 , the turbine engine 2-3 may be directly connected toan input end of the reduction gearbox 2-2. The reduction gearbox 2-2, insome example implementations, may be integrated as part of thefracturing pump 2-1. An input speed of the reduction gearbox 2-2 of thefracturing pump 2-1 may be configured to match an output speed of theturbine engine 2-3. Further, an input torque of the reduction gearbox2-2 of the fracturing pump 2-1 may be configured to match an outputtorque of the turbine engine 2-3. A particular example construction andconfiguration of the reduction gearbox 2-2 is described in more detailbelow. Such direction connection of the reduction gearbox 2-2implementation with the turbine engine 2-3 thus simplifies thetransmission device between the fracturing pump 2-1 and the turbineengine 2-3. In other words, a transmission shaft or a coupling may beomitted, greatly shortening the total length of the power drive systemfor the fracturing pump 2-1. In the example of FIG. 2 , the turbineengine 2-3 is used as the power source, the transmission device isimplemented as the reduction gearbox 2-2 which may be equipped orintegrated on the fracturing pump 2-1 itself, and the fracturing pump2-1 is also pre-fitted together with turbine engine 2-3. As such, thepower drive system for the fracturing pump is configured as a simplestructure that is easy to maintain.

As shown in the implementation of FIG. 2 , the fracturing pump 2-1, theturbine engine 2-3 and the exhaust system (including the exhaust duct2-4 and silencer 2-5 as described below) may be disposed in a straightline along the transmission direction of mechanical power.

The exhaust system illustrated in FIG. 2 may include an exhaust duct 2-4and an exhaust silencer 2-5. As shown in FIG. 2 , one end of the exhaustduct 2-4 may be connected to the exhaust silencer 2-5, and the other endof the exhaust duct 2-4 may be connected to an exhaust port of theturbine engine 2-3.

The configuration in which the fracturing pump 2-1, the turbine engine2-3, the exhaust duct 2-4 and the exhaust silencer 2-5 are disposed in astraight line along the transmission direction of power may particularlyhelp avoid excessive transmission power loss that may be associated withmore complex transmission mechanisms for direction change of themechanical power, thus enabling efficient transmission performance ofthe fracturing equipment.

FIG. 3 and FIG. 4 shows an example of a turbine-based fracturing systemincluding the turbine engine, reduction gearbox, and plunge pumpconfiguration of FIG. 2 . FIG. 3 particular shows such a fracturingsystem being disposed on a semi-trailer in a resting mode for operationor storage whereas FIG. 4 shows the same fracturing system disposed onthe semi-trailer, with the semi-trailer being attached to a tractor in atransportation mode. FIGS. 5-10 shows an example construction of aplunger pump and an example construction of the reduction gearbox thatmay be integrated with the plunger pump.

As shown in FIG. 3 , the semi-trailer-loaded turbine fracturing systemmay include a transporter 3-200, an exhaust system, a turbine engine3-500 and a plunger pump 3-600. The turbine engine 3-500 functions asthe mechanical power source for the power transmission system of thewhole equipment, which may be directly fueled by 100% natural gas ratherthan other types of fuels, which greatly reduce the operational costcompared with the cost of diesel consumption in a diesel-driven systemand the cost of having to invest on gas generator sets in theelectricity driven fracturing system. Alternatively, the turbine engine3-500 can also use 100% oil or other liquid fuel if needed.

As further shown in FIG. 3 , the exhaust system may be connected to anexhaust port of the turbine engine 3-500. An output end of the turbineengine 3-500 may be connected to the plunger pump 2-600. The poweroutput end and the exhaust system may be disposed on two opposite endsof the turbine engine 3-500. The exhaust system, for example, mayinclude an exhaust silencer 3-300 and an exhaust duct 3-400. The exhaustsilencer 3-300 may be connected to the exhaust port of the turbineengine 3-500 through the exhaust duct 3-400. The exhaust duct 3-400 maybe used to direct the exhaust (e.g., combustion exhaust) of the turbineengine 3-500 into the exhaust silencer 3-300, which can reduce the noisefrom the exiting combustion exhaust of the turbine engine 3-500. Asshown in FIG. 3 , the exhaust system (including the exhaust silencer3-300 and the exhaust duct 3-400), the turbine engine 3-500, and theplunger pump 3-600 may be disposed in a straight line along thetransmission direction of the mechanical power, so as to avoid excessivetransmission loss, and to enable an efficient transmission performanceand to further lower the center of gravity of the equipment for improvedoperational and transportation safety and stability.

As shown in FIG. 3 , the transporter 3-200 (or the main semi-trailerplatform) may be used to support and at affix the exhaust system, theturbine engine 3-500 and the plunger pump 3-600. As further shown inFIG. 5 , the plunger pump 3-600 may include a power end assembly 5-1, ahydraulic end assembly 5-2 and a reduction gearbox assembly 5-3 (asintegrated in the plunger pump assembly). One end of the power endassembly 5-1 may be connected to the hydraulic end assembly 5-2. Theother end of the power end assembly 5-1 may be connected to thereduction gearbox assembly 5-3. The reduction gearbox assembly 5-3 mayinclude one or more planetary reduction gearsets (or gearboxes) and oneor more parallel reduction gear sets (or gearboxes). The planetaryreduction gear sets (or gearboxes) may be used in conjunction with theparallel reduction gear sets (or gearboxes) to obtain a transmissionratio of 60:1 to 106:1. The turbine engine 3-500 may be connected to thereduction gearbox assembly 3-3 (or 5-3). The reduction gearbox assembly3-3/5-3 may be used to slow down the rotational speed and increase thetorque of the power output of the turbine engine 3-500 for driving theplunger pump 3-600. The transporter 3-200 may be further provided withcomponents disposed thereon such as batteries, wiring/cabling, a fueltank, a lubricating oil tank, a hydraulic oil tank and the like,providing lubrication and/or cooling service and support to the othercomponents such as the turbine engine 3-500, the plunger pump 3-600, andthe like.

In some example implementations as shown in FIGS. 5-10 , there may betwo planetary reduction gearboxes in the reduction gearbox assembly 3-3(or 5-3), including a first planetary reduction gearbox 6-9 and a secondplanetary reduction gearbox 6-11. One end of the first planetaryreduction gearbox 6-9 may be connected to a crankshaft 10-7 of the powerend assembly 5-1. The other end of the first planetary reduction gearbox6-9 is connected to the parallel reduction gearbox 6-10. The other endof the parallel reduction gearbox 6-10 may be connected to the secondplanetary reduction gearbox 6-11. The other end of the second planetaryreduction gearbox 6-11 may be connected to the transmission shaft of theturbine engine 3-500. When in operation, the kinetic energy transferredby the transmission shaft of the turbine engine 3-500 is first reducedin rotational speed by the second planetary reduction gearbox 9-11, andis then decreased in rotational speed by the parallel reduction gearbox6-10, and finally decreased om rotational speed by the first planetaryreduction gearbox 6-9 for a third time.

For example, the transmission ratio of the reduction gearbox assembly3-3 may be designed and adjusted to elevate the maximum input speed(e.g., increasing from the current 2100 rpm to 16000 rpm). Theconnection between the current turbine engine 3-500 and the plunger pump3-600 through two reduction gearboxes and one transmission shaft isimproved so that the turbine engine 500 can be directly connected to thereduction gearbox assembly 3-3 on the plunger pump 3-600, which not onlysatisfies the rotation speed reduction requirements, but also simplifiesthe transmission and driving structure of the whole fracturingequipment. Such implementations help reduce the length dimension or thesystem and provide a system that is of lower cost and is easier tomanage, maintain and transport.

The example above using two sets of planetary gearboxes and a parallelgearset in between enables transmitting the output rotation of theturbine engine to the plunger pump without direction change but with anoffset. In particular, the rotational axis of the turbine engine outputis parallel to the same rotational direction of the input end of theplunger pump but not coaxial. The rotational axis of the plunger pumpmay refer to a rotational axis of the crankshaft 10-7 within a crankcase9-4 of the plunger pump as described in further detail below. The offsetbetween the rational axis of the output of the turbine engine and therotational axis of the input of the plunger pump may be determined bythe distance between the center of the first planetary gearbox 6-9 andthe center of the second planetary gearbox 6-11 as shown in FIG. 6 . Theoffset, for example may be configured in the horizontal plane, such thatthe shift of rotational axis between the turbine engine and the input ofthe plunger pump is in the horizontal plane rather that being a verticaloffset. In some other implementations, the offset between the rotationalaxis of the turbine engine and the axis of the plunger pump may be morein the horizontal direction than vertical direction (e.g., a planeformed by these two rotational axes may be less than 45 degrees from thehorizontal plane when the fracturing system is in operation. In such amanner, the rational center of the entire turbine engine and plungerpump system need to rise vertically. The center of gravity of the entiresystem thus may be kept low, thereby increasing operational andtransportation safety.

As an example of the planetary gearboxes above and as shown in FIG. 7 ,The planetary reduction gearbox may include one sun gear 7-16, fourplanetary gears 7-14 and one gear ring 7-15. The four planetary gears7-14 may form a planetary gear mechanism. The sun gear 7-16, forexample, may be located at the center of the planetary gear mechanism.The planetary gears 7-14 and the adjacent sun gear 7-16 and gear ring7-15 may be in configured in a normally engaged state. The exampleplanetary reduction gearbox of FIG. 7 may use four (or other number of)evenly distributed planetary gears 7-14 to transmit motion and powersimultaneously. The centrifugal inertia force generated from therevolution of the four planetary gears 7-14 offsets the radial componentof a counterforce between the tooth contours, thereby reducing the forceon the main shaft and helping achieve high power transmission.

As shown in FIG. 8 , the parallel reduction gearbox 6-10 may include apinion 8-13 and a bull gear 8-12. The pinion 8-13 may be coaxial withthe sun gear 7-16 of the first planetary reduction gearbox 6-9, and thebull gear 8-12 may be coaxial with the sun gear 7-16 of the secondplanetary reduction gearbox 6-11. The mechanical power generated by theturbine engine is transmitted to the bull gear 8-12 through the pinion8-13 in the parallel reduction gearbox 6-10 to realize the reduction.

In some example implementation, an input angle of the reduction gearboxassembly 3-3 can be adjusted according to input requirements.

While the example above in FIGS. 3-8 shows a direct drive of the plungerpump by the turbine engine via the reduction gearbox without otherdriving shafts, in some other example implementations, with respect toFIG. 5 , the other end of the power end assembly 5-1 may be connected tothe reduction gearbox assembly 5-3 through a spline or a flexiblecoupling.

As shown in FIG. 9 , the power end assembly 5-1 of the plunger pump maybe s designed to be a segmented structure so that the power end assembly5-1 has a compact overall structure and can be manufactured in an easymanner, and that the assembly and maintenance of the whole plunger pumpbecome more convenient. In the meanwhile, the processing cost may bereduced.

The power end assembly 5-1 may include a crankcase 9-4, a crosshead case9-5 and a spacer frame 9-6. One end of the crosshead case 9-5 may beconnected to the crankcase 9-4, whereas the other end of the crossheadcase 9-5 may be connected to the spacer frame 9-6. In someimplementations, the hydraulic end assembly 5-2 may be disposed at oneend of the spacer frame 9-6 and may be connected to the crankcase 5-4through bolts sequentially passing through the spacer frame 9-6 and thecrosshead case 9-5. The reduction gearbox assembly 5-3 may be connectedto the crankcase 9-4 through bolts. The crankshaft 10-7 in the crankcase9-4 may be forged from alloy steel or other materials and may includesix or other number of axle journals 10-7 and five or other number ofbellcranks 10-8. One bellcrank 10-8 may be disposed between every twoadjacent axle journals 10-7, yielding an example design of afive-cylinder structure. The design of the five-cylinder structure helpsincrease the output displacement of the plunger pump 3-600. Compared toa three-cylinder pump, the five-cylinder pump operates more smoothlywith less vibration, thus reducing the vibration of the whole plungerpump and prolonging its service life. The distance between the center ofrotation of the bellcrank 10-8 and the center of rotation of thecrankshaft 10-7 may be set at 120 to 160 mm. The distance between thecenter of rotation of the bellcrank 10-8 and the center of rotation ofthe crankshaft 10-7 may be further adjusted to increase the maximumpower of the plunger pump 3-600 to 5000-7000 hp, so that the plungerpump 3-600 can output a fracturing fluid of higher pressure, via a longplunging stroke. For example, the resulting plunging stroke may reach10-12 inches. A large displacement of the fracturing liquid for thefracturing operation may be achieved, with a number of strokes of thepump being reduced, thereby further extending the service life of thecomponents.

In some implementations, as shown in FIG. 4 , the transporter 3-200 mayinclude a chassis which is provided with a transport section, a bearingsection and a lapping section which are connected in sequence. When theturbine fracturing equipment is in operation, the bearing section of thechassis can contact with the ground to provide a stable support. Whenthe turbine fracturing equipment is in transport state, the bearingsection of the chassis does not contact the ground and the lappingportion 4-210 of the transporter 3-200 may be attached to tractor 4-700and the semi-trailer platform inclines upwards towards the lappingportion 4-210.

The transporter 3-200 may include wheels and axles. The wheels, forexample, may be disposed at both ends of the axles. The axles may beconnected to the chassis, the number of the axles may be 3 or above toprovide a sufficient bearing capacity. The axles may be disposed at thetransport section of the chassis.

As shown in FIG. 4 , when the turbine fracturing equipment is inoperation, the bottom of the bearing section of the chassis may be atthe same level as the bottom of the wheels. The bottom of the bearingsection may include a horizontal surface 4-230 plus a sloped surface4-240 when the turbine fracturing equipment is in operation. Thehorizontal surface 230 at the bottom of the bearing section may beconfigured to be in full contact with the ground to increase thestability of the equipment in operations. The sloped surface 4-240allows the raised chassis to be lifted off the ground for easyattachment to the tractor 4-700 when the turbine fracturing equipment isbeing transported.

As shown in FIG. 4 , the bottom of the lapping section may be providedwith a bevel 4-210 which may be further provided with a bulge 4-220.While the turbine fracturing equipment is being transported, the bevel4-210 may be used in conjunction with external towing equipment, thebulge 4-220 may be configured to assist in fixing the transporter 4-200on the external towing equipment and preventing the transporter 4-200from separating from the external towing equipment. The external towingequipment may be a tractor 4-700, and the bulge 4-220 may be implementedas a traction pin used in conjunction with the tractor 4-700.

As shown in either FIG. 3 or FIG. 4 , the transporter 4-200 may befurther provided with a hydraulic power unit 3-100 which may be used todrive the hydraulic system on the turbine fracturing semi-trailer. Thehydraulic system may include a hydraulic pump, a hydraulic motor,various valves, a hydraulic oil tank, a hydraulic oil radiator, and thelike. The hydraulic system may be mainly used to drive the fuel pump ofthe turbine engine 3-500, the starting motor of the turbine engine3-500, the lubrication system of the power end assembly 5-1 of theplunger pump 3-600, the lubrication system of the reduction gearboxassembly 5-3 of the plunger pump 3-600, and various oil radiators, andthe like.

The hydraulic power unit 3-100 may be driven by a diesel engine ordriven by an electric motor. The hydraulic power unit may be disposed ona gooseneck portion of the transporter, as shown in FIG. 3 and FIG. 4 .

The transporter 3-200 may be further provided with a cooling systemwhich cools the oil used on the turbine fracturing semi-trailer. The oilused may include but is not limited to the engine oil for the turbineengine 3-500, hydraulic oil, the lubricating oil for the plunger pump3-600, and the like. The cooling system may be located on the gooseneckportion of the transporter, as shown in FIGS. 3-4 .

In some implementations, the engine oil, the hydraulic oil, orlubrication oil may be circulated from the hydraulic system disposed onthe gooseneck section of the transporter 3-200 to the co-located coolingsystem and then to the turbine engine 3-500 or the reduction gearbox3-3, or the plunger pump 3-600, and then back to the hydraulic unit.Alternatively, the engine oil or lubrication oil may be circulated fromthe hydraulic system disposed on the transport section/gooseneck sectionof the transporter 3-200 to the turbine engine 3-500 or the reductiongearbox 3-3, or the plunger pump 3-600, and then to the cooling system,and back to the hydraulic unit.

FIGS. 11 and 12 show another example implementation of the turbine-basedfracturing equipment affixed on a semi-trailer platform. As shown inFIGS. 11 to 12 , similar to the implementations above, a turbinefracturing equipment may include a transporter 11-2, a turbine engine11-5, a reduction gearbox 11-6, a transmission mechanism 11-7 and aplunger pump 11-8. The turbine engine 11-5 functions as the power sourcefor the power transmission system of the whole fracturingequipment/system. An output end of the turbine engine 11-5 may beconnected to one end of the reduction gearbox 11-6. The other end of thereduction gearbox 11-6 may be connected to the plunger pump 11-8 throughthe transmission mechanism 11-7 rather than directly (similar to theexample implementation of FIG. 1 ). The transporter 11-2 may be used tosupport the turbine engine 11-5, the reduction gearbox 11-6, thetransmission mechanism 11-7 and the plunger pump 11-8. The transporter11-2 may include a chassis provided with a transport section, a bearingsection and a lapping section which may be connected in sequence. Whenthe turbine fracturing equipment is in operation, the bearing section ofthe chassis may be in contact with the ground. When the turbinefracturing equipment is in a transport state, the bearing section of thechassis does not contact the ground. The chassis may be further providedwith components such as batteries, wiring/cabling, a fuel tank, alubricating oil tank, a hydraulic oil tank and the like for providingservice and support for the other fracturing components such as theturbine engine 11-5, the reduction gearbox 11-6, the plunger pump 11-8and the like. The reduction gearbox 11-6 is used to slow down therotational speed and increase the torque of the power output of theturbine engine 11-5 for driving the plunger pump 8 through thetransmission mechanism 11-7.

In some implementation, as shown in FIG. 11 , the turbine fracturingequipment/system may further include a vertical support 11-15 betweenthe exhaust duct and the turbine engine 11-5, wherein the verticalsupport 11-15 is disposed on and in direct physical contact with a topsurface of the chassis.

In some implementations, the transporter 11-2 may include wheels andaxles. The wheels may be disposed at both ends of the axles. The axlesmay be connected to the or more chassis., to provide an adequate bearingcapacity.

In some implementations, the axles may be disposed at the transportsection of the chassis (e.g., towards the rear of the chassis).

As shown in FIG. 12 , when the turbine fracturing equipment is inoperation, the bottom of the bearing section of the chassis may bedesigned such it is at the same level as the bottom of the wheels. Thebottom of the bearing section may include a horizontal surface 12-12plus a sloped surface 12-13 when the system is in operation. Thehorizontal surface 12-12 at the bottom of the bearing section may be infull contact with the ground when in operation, thereby increasing theoperating stability of the equipment. The sloped surface 12-13 allowsfor the chassis, when being raised at the lapping section, to be liftedoff the ground for attachment with the traction 12-9 when the turbinefracturing equipment is in a transport state.

As shown in FIG. 12 , the bottom of the lapping section may be furtherprovided with a bevel 12-10 which is further provided with a bulge12-11. When the turbine fracturing equipment is in the transport state,the bevel 12-10 can be used in conjunction with the external towingequipment such as the traction 12-9. The bulge 12-11 may assist infixing the transporter 11-2 onto and preventing the transporter 11-2from separating from the external towing equipment. The external towingequipment may be the tractor 9 and the like, and the bulge may beimplemented in the form of a traction pin.

The turbine engine 11-5 may be provided with an exhaust system on anopposite side of the reduction gearbox 11-6. The exhaust system mayinclude an exhaust silencer 3 and an exhaust duct 11-4. The exhaustsilencer 11-3 may be connected to an exhaust port of the turbine engine11-5 through the exhaust duct 11-4. The exhaust duct 11-4 may beconfigured to direct the combustion exhaust of the turbine engine 11-5into the exhaust silencer 11-3, which can reduce the noise of theexhaust exiting from the exhaust system.

As shown in FIGS. 11 and 12 , the exhaust system, the turbine engine11-5, the reduction gearbox 11-6, the transmission mechanism 11-7 andthe plunger pump 11-8 are disposed in a straight line along thetransmission direction of power. The linear connection of the turbineengine 11-5, the reduction gearbox 11-6, the transmission mechanism 11-7and the plunger pump 11-8 along the transmission direction of power canhelp reduction of excessive transmission loss, thus resulting inefficient transmission performance. The turbine engine 11-5 itself hasthe advantages of small volume, light weight and high-power density. Forthe same size and weight, the unit-power generation of a turbinefracturing equipment can be more than twice that of conventional dieselfracturing equipment. The turbine engine 11-5 can be fueled by 100%natural gas directly, greatly reducing the use cost compared with thediesel consumption in diesel drive and the cost of investment on gasgenerator sets of electric drive fracturing equipment. Of course, theturbine engine 11-5 can also use 100% fuel oil or another liquid fuel.As shown in FIG. 11 , the turbine fracturing equipment may be configuredto for a turbine engine to drive a plunger pump in a one-to-one mannerrather than using a single power source to drive multiple plunger pumps,such as the scheme used in traditional electricity driven fracturingequipment, where a single high-power gas generator set is used to drivemultiple plunger pumps. Multiple set of the turbine fracturingequipment/system described above may be operated collaboratively at awell site to avoid singe point failure and to distribute failure risk toeach turbine fracturing equipment/system.

In some example implementations, the transmission mechanism 11-7 may beimplemented as a transmission shaft or another type of coupling.

As shown in FIGS. 11 and 12 , a hydraulic power unit 11-1 may bedisposed on the transport section (e.g., the gooseneck section). Thehydraulic power unit 11-1 may be used to drive the hydraulic system onthe turbine fracturing equipment. The hydraulic system may include ahydraulic pump, a hydraulic motor, various valves, a hydraulic oil tank,a hydraulic oil radiator, and the like. The hydraulic system may be usedto drive the fuel pump of the turbine engine 11-5, the starting motor ofthe turbine engine 11-5, the lubrication system at the power end of theplunger pump 11-8, the lubrication system of the reduction gearbox 11-6,and various oil radiators, and the like.

In some example implementations, the hydraulic power unit 11-1 may bedriven by a diesel engine or driven by an electric motor.

As shown in FIGS. 11 and 12 , a cooling system may be collocated withthe hydraulic power unit on the transport section (e.g., the goosenecksection). The cooling system may be configured to cool the oil used onthe turbine fracturing equipment. The oil used includes the engine oilfor the turbine engine 11-5, hydraulic oil, the lubricating oil for theplunger pump 8, the lubricating oil for the reduction gearbox 11-6, andthe like. In some implementations, the engine oil or lubrication oil maybe circulated from the hydraulic system disposed on the transportsection/gooseneck section of the transporter 11-2 to the cooling systemand then to the turbine engine 11-5 or the reduction gearbox 11-6, orthe plunger pump 11-8, and then back to the hydraulic unit.Alternatively, the engine oil or lubrication oil may be circulated fromthe hydraulic system disposed on the transport section/gooseneck sectionof the transporter 11-2 to the turbine engine 11-5 or the reductiongearbox 11-6, or the plunger pump 11-8, and then to the cooling system,and back to the hydraulic unit.

In some implementations of FIGS. 11-12 , the power of the plunger pump11-8 may be configured at 5000 hp or above. The higher the power of theplunger pump 11-8 is, the more suitable it is for lone-time andhigh-load continuous operation conditions.

It will be appreciated to persons skilled in the art that the presentinvention is not limited to the foregoing embodiments, which togetherwith the context described in the specification are only used toillustrate the principle of the present invention. Various changes andimprovements may be made to the present invention without departing fromthe spirit and scope of the present invention.

For example, as a variation of FIG. 11 , the reduction gearbox may belocated on the other side of the transmission device 11-7, in directcoupling with the plunger pump 11-8 or may be integrated with theplunger pump. In such variation, the end of the transmission device 11-7that is connected to the reduction gearbox 11-6 may be instead directcoupled to the output end of the turbine engine 11-5.

For another example, as a variation of FIG. 11 , an additional reductiongearbox may be integrated with the plunger pump 11-8. The transmissiondevice 11-7 thus may be coupled to the integrated reduction gearbox onone side and the reduction gearbox 11-6 on the other end. Theconfiguration with two reduction gearbox assemblies may help simplydesign of each of the reduction gearbox to achieve the rotational speedreduction and torque increase needed for the turbine engine to drive theplunger pump.

For another example, the positions of the various components disposed onthe semi-trailer platform or the transporter are not limited by thedisclosure above. For example, the plunger pump may be disposed towardseither end of the transporter (in FIG. 1 the plunger pump is disposedtowards the rear of the semi-trailer whereas the plunger pump of FIG. 3or FIG. 11 is disposed towards the front of the transporter). Likewise,the gooseneck section of the transporter or the semi-trailer body may belocated either in the front or rear end of the transporter or thesemi-trailer body (e.g., the gooseneck portion is at the front end inFIG. 1 , whereas the gooseneck portion is at the rear end in FIG. 3 andFIG. 11 ). When the gooseneck portion is in the front end, it may alsofunction as a lapping section having the bulge in the form of, forexample, a traction pin, as described above, for attachment to a towingequipment (e.g., a tractor).

All these and other changes and improvements shall fall within theprotection scope of the present invention. The protection scope of thepresent invention is defined by the appended claims and equivalentsthereof.

What is claimed is:
 1. A turbine fracturing semi-trailer system,comprising: a turbine engine comprising a rotational output endassociated with a first rotational axis; at least one first reductiongearbox assembly comprising a first planetary gearset engaging aparallel gearset engaging a second planetary gearset, the firstplanetary gearset and the second planetary gearset being associated witha second rotational axis and a third rotational axis, respectively; anda plunger pump comprising a crankcase associated a fourth rotationalaxis; wherein: the turbine engine, the at least one first reductiongearbox assembly and the plunger pump are sequentially disposed; thefirst rotational axis is colinearly aligned and coupled to the secondrotational axis; the third rotational axis is colinearly aligned andcoupled to the fourth rotational axis; and the first rotational axis andthe fourth rotational axis are offset from one another more horizontallythan vertically when the turbine fracturing semi-trailer system is in anoperational state.
 2. The turbine fracturing semi-trailer systemaccording to claim 1, wherein the at least one first reduction gearboxassembly is integrated with the plunger pump.
 3. The turbine fracturingsemi-trailer system according to claim 2, further comprising atransmission device disposed between the turbine engine and the at leastone first reduction gearbox assembly.
 4. The turbine fracturingsemi-trailer system according to claim 2, further comprising a secondreduction gearbox assembly disposed between the turbine engine and theat least one first reduction gearbox assembly.
 5. The turbine fracturingsemi-trailer system according to claim 4, further comprising atransmission device disposed between the at least one first reductiongearbox assembly and the second reduction gearbox assembly.
 6. Theturbine fracturing semi-trailer system according to claim 5, wherein thetransmission device comprises a single rotational shaft.
 7. The turbinefracturing semi-trailer system according to claim 1, wherein: theturbine engine further comprises an exhaust system disposed on anopposite end of the turbine engine from the at least one first reductiongearbox assembly; and the exhaust system comprises an exhaust silencerand an exhaust piping, the exhaust silencer is communicated with anexhaust port of the turbine engine through the exhaust piping.
 8. Theturbine fracturing semi-trailer system according to claim 7, wherein theexhaust system, the turbine engine, the at least one first reductiongearbox assembly, and the plunger pump are sequentially disposed in astraight line along a transmission direction of rotational power.
 9. Theturbine fracturing semi-trailer system according to claim 1, wherein: anair intake system is disposed above the turbine engine; the air intakesystem comprises a plurality of air intake filters, an air intakesilencer, and an air intake duct; one end of the air intake silencer isconnected to the plurality of air intake filters; the other end of theair intake silencer is connected to one end of the air intake duct; andthe other end of the air intake duct is connected to an air intake portof the turbine engine.
 10. The turbine fracturing semi-trailer systemaccording to claim 9, wherein the plurality of air intake filters aredisposed on two sides of the air intake system along a direction ofpower transmission of the turbine fracturing semi-trailer system andextend at least an entire length of the turbine engine.
 11. The turbinefracturing semi-trailer system according to claim 10, further comprisinga plurality of inertia separators coupled to the plurality of air intakefilters for separating solid particles and liquid droplets from airinflow into the air intake system.
 12. The turbine fracturingsemi-trailer system according to claim 1, wherein output power of theplunger pump is 5000 hp or above.
 13. The turbine fracturingsemi-trailer system according to claim 1, further comprising asemi-trailer body, wherein the turbine engine, the at least one firstreduction gearbox assembly and the plunger pump are sequentiallydisposed on the semi-trailer body, and 3 or more axles are installedbeneath the semi-trailer body, and each axel is installed with at leasta pair of wheels.
 14. The turbine fracturing semi-trailer systemaccording to claim 1, further comprising a hydraulic power unit disposedon a gooseneck portion at one end of the semi-trailer body, thehydraulic power unit is configured to drive a hydraulic system in theturbine fracturing semi-trailer system.
 15. The turbine fracturingsemi-trailer system according to claim 14, wherein the hydraulic powerunit is driven by a diesel engine or driven by an electric motor. 16.The turbine fracturing semi-trailer system according to claim 14,wherein a cooling system is collocated with the hydraulic power unit onthe gooseneck portion of the semi-trailer body, the cooling system beingconfigured to cool engine oil or lubrication oil displaced by thehydraulic power unit for an operation of the turbine engine, the atleast one first reduction gearbox assembly, or the plunger pump.
 17. Theturbine fracturing semi-trailer system according to claim 1, wherein thecrankcase of the plunger pump comprises at least 6 axle journals and atleast 5 bellcranks.
 18. The turbine fracturing semi-trailer systemaccording to claim 17, wherein a distance between a first center ofrotation of the at least 5 bellcranks and a second center of rotation ofa crankshaft of the crankcase is between 120 and 160 mm.
 19. The turbinefracturing semi-trailer system according to claim 18, wherein a plungingstroke of the plunger pump is between 10 and 12 inches when being inoperation.
 20. The turbine fracturing semi-trailer system according toclaim 1, further comprising a semi-trailer body, wherein: the turbineengine, the at least one first reduction gearbox assembly and theplunger pump are sequentially disposed on the semi-trailer body; theplunger pump is disposed on a lapping section of the semi-trailer body;and the lapping section is configured with a traction pin for attachmentto a towing equipment for the turbine fracturing semi-trailer system.